System for converting heat to kinetic energy

ABSTRACT

A system for converting heat to kinetic energy, characterized by a fluid-driven motor responsive to an introduction of highpressure fluid for driving a selected power train, and a pressure generator for introducing the high-pressure fluid to the motor. The pressure generator includes a plurality of boiler tubes for receiving low-pressure fluid, a fire-box for successively transferring heat to the boiler tubes, and a pressure equalizer for incrementally equalizing pressures within boiler tubes, whereby an introduction of low-pressure fluid, followed by an efficient conversion to a high-pressure fluid, is facilitated within the system.

Waited fitates Patent m Mushines 1 3,?33fii9 1 May 22,1973

Primary ExaminerMartin P. Schwadron Assistant Examiner-H. Burks, Sr.Att0meyl-luebner & Worrel {5 7] ABSTRACT A system for converting heat tokinetic energy, characterized by a fluid-driven motor responsive to anintroduction of high-pressure fluid for driving a selected power train,and a pressure generator for introducing the high-pressure fluid to themotor. The pressure generator includes a plurality of boiler tubes forreceiving low-pressure fluid, a fire-box for successively transferringheat to the boiler tubes, and a pressure equalizer for incrementallyequalizing pressures within boiler tubes, whereby an introduction oflowpressure fluid, followed by an efficient conversion to ahigh-pressure fluid, is facilitated within the system.

13 Claims 10 Drawing Figures PATENIED HAY 2 2197s SHEET 1 BF 4 ANTHONYMUSH/NES IIVVEN ro/e m 7M A TTORNE) PATENTED W 22 [975 3,733,819

SHEET 3 OF 4 ANTHONY MUSH/NES IN VEN TOP WfM ,4 TTORNEVS BACKGROUND OFTHE INVENTION The invention generally relates to an energy conversionsystem and more particularly to an improved system for converting heatto kinetic energy.

Numerous systems heretofore have been employed in converting heat tokinetic energy. Normally, such systems include a steam boiler wherein aliquid is converted to a vapor and admitted to a cylinder of apistontype motor, or to a turbine, where it expands against the piston,or against turbine blades, as the case may be, discharged therefrom andthence returned via a feed pump to the boiler.

In employing systems of known designs, difficulty often is encounteredin introducing the working fluid in its liquid phase, into a boilerpreparatory to its being converted to its vapor phase in response to anapplication of heat. This results from system back-pressure whichnormally attends the introduction of the fluid into the boiler.Consequently, numerous and complex systems hereto have been utilize'd'inan effort to overcome this difficulty. Of course, where a conversionsystem is employed with a prime mover of a type utilized in anenvironment which imposes design limitations on both the mass and bulkof the system, simplicity attains a particular place of prominence amongprevailing design parameters.

Attending the increased use of working fluids employed in the field ofcryogenics is the prevailing interest in the development of conversionsystems which can be employed efficiently in driving vehicles includingautomobiles and the like. However, systems employed for this purposenecessarily must be substantially simplified.

OBJECTS AND SUMMARY OF THEINVENTION It is therefore an object of theinstant invention to provide a simplified system for converting heat tokinetic energy.

It is another object to provide an improved system which employs energyof heat for imparting driven motion to a selected power train.

It is another object to provide in a system for converting heat tokinetic energy an improved pressure generator wherein substantialeffects of back-pressure are eliminated as a working fluid is introducedinto the generator.

It is another object to provide in a system for converting heat tokinetic energy a pressure generator for simultaneously receiving aworking fluid in a liquid phase, heating the working fluid to effect aphase change, and pressure equalizing means for incrementally elevatingthe pressure of the working fluid in its liquid phase, preparatory toits achieving a vapor phase, while circumventing deleterious effects ofsystem back-pressure.

These and other objects and advantages are achieved through the use ofan energy conversion system which utilizes a pressure-responsive motorand a pressure generator having a plurality of sequentially heatedboiler tubes interconnected through a rotating pressure-transfer valvethrough which the boiler tubes sequentially are connected in variablepairs, so that as a working fluid is introduced pressures simultaneouslyare developed and reduced within the generator through a continuousexchange of pressures between boiler tubes for thereby avoiding theeffects of system back-pressure.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a diagrammatic view, not toscale, of a system embodying the principles of the instant invention,including a vapor generator, a turbine associated with the generator,and a condenser for converting a working fluid to its vapor phase.

FIG. 2 is a fragmentary plan view of the vapor generator shown in FIG.1.

FIGS is a sectioned elevation of the vapor generator shown in FIGS. 1and 2.

FIG. 4 is a partially sectioned, perspective view of the vapor generatorshown in FIGS. 1, 2 and 3.

FIG. 5 is a fragmentary plan view of a pressure equalizer employed bythe vapor generator.

FIG. 6 is a sectioned plan view of a valve employed by the pressureequalizer.

FIG. 7 is a sectioned elevation of the valve shown in FIG. 6.

FIG. 8 is a schematic view of a modified form of a pressure equalizeremployable with the generator.

FIG. 9 is a schematic view of a further embodiment of the instantinvention.

FIG. '10 is a sectioned elevation of the valve employed in equalizingpressures developed in the system shown in FIG. 9.

DESCRIPTION OF THE PREFERRED EMBODIMENTS (GENERAL DESCRIPTION) Referringnow to the drawings wherein like reference characters designate like orcorresponding parts throughout the several views, there is shown in FIG.1 a system which embodies the principles of the instant invention.

The system includes a vapor generator, generally designated 10, coupledwith a prime mover, such as a turbine, generally designated 12. Acondenser, generally designated 14, is coupled between the output sideof the turbine 12 and the input side of the vapor generator 10. Where sodesired, a feed pump 16 is interposed between the condenser and thevapor generator for assuring that a flow of working fluid therebetweenis maintained for insuring a constant delivery of working fluid to thegenerator 10. While various substances can be employed as a workingfluid, Freon functions satisfactorily for this purpose. It is, however,to be understood that the working fluid must be capable of undergoingphase changes between a vapor and a liquid with minimal heat exchange.

As a practical matter, a plurality of conduits 18 formed of any suitablematerial and of a size sufficient for delivering the working fluid, inits liquid phase, as well as in itsvapor phase, is employed in couplingthe vapor generator 10, the prime mover l2, and the condenser 14 into anintegrated and operative system.

As a practical matter, the particular prime mover 12 employed is amatter of convenience, therefore, a detailed description of the turbine12 is omitted in the interest of brevity. Similarly, since the condenser14 and the feed pump 16 are well within the purview of the art,

a detailed description thereof also is omitted. It is to be understood,of course, that the vapor generator 16) serves as a source of heatedfluid, preferably a vapor,

which is directed through the prime mover 12 for imparting motionthereto. From the prime mover, the vapor is delivered to the condenser14 whereupon the working fluid is converted to its liquid phase andreturned to the vapor generator via the pump 16.

The rate at which motion is imparted to the prime mover 12 is dictated,in part, by the pressure of the working fluid as it is deliveredthereto. Where so desired, a throttle valve is provided for controllingthe rate of flow of fluid, and thus its pressure, as it is deliveredfrom the vapor generator 10 to the prime mover 12. The valve 20 is of acommercially available and suitable design which serves to control theflow of fluid as it is passed therethrough. Accordingly, it is to beunderstood that once the system of the instant invention is renderedoperative, a vapor, under pressure, is delivered via the valve 20 to theturbine 12, whereupon the turbines output shaft, not designated, isdriven in rotation in a manner and at a determinable rate consistentwith the operation of commercially available turbines. Hence, it will beappreciated that by manipulating the valve 20, the rate of rotationimparted to the output shaft of the prime mover 12 accurately iscontrolled.

As a practical matter, the condenser 14 serves to transfer heat from theworking fluid, prior to its delivery to the feed pump 16. While thecondenser 14 is H- lustrated as including a serpentine conduit, it is tobe understood that conduits of any configuration including helical coilsand the like can be employed equally as well for transferring heat fromworking fluid as it is conducted therethrough for undergoing conversionto its liquid phase. Similarly, auxiliary cooling devices, such as fansand the like, also may be employed for transferring heat from theworking fluid to a flowing stream of air passed through the condenser14.

The pump 16 is capable of establishing a standing flow of working fluidat selected pressures. Since the fluid being delivered from thecondenser 14 to the pump 16 frequently is a mixture of gas and liquid,the pump 16 preferably is of a type suitable for accelerating the fluidin either of its phases as it passed therethrough. Since such pumps arewell known, commercially available, and well within the skill of theart, a detailed description of the pump employed in the system isomitted.

In view of the foregoing, it should readily be apparent that the workingfluid employed in driving the prime mover 12 is converted to its vaporphase and pressurized within the vapor generator 10, directed throughthe prime mover 12 for imparting motion thereto, cooled within thecondenser 14 and reintroduced into the vapor generator, in its liquidphase. Thus, the heat applied to the working fluid in the vaporgenerator is utilized as a source of kinetic energy.

VAPOR GENERATOR (First Form) As illustrated in FIGS. 1 through 8, oneform of the vapor generator 10 includes a housing 22 of a generallycircular configuration supported by a plurality of mounting brackets 24.These are employed in supporting the housing 22 in suspension from anyselected structure or vehicle. It is to be understood that the housing22, of course, can be supported at locations other than as illustratedin FIGS. 1 and 3. Accordingly, the particular mounting structure for thehousing 22 is deemed a matter of convenience, dictated by the nature ofthe structure with which the system of the instant invention isemployed.

Similarly, the particular materials employed in fabricating the housing22 also is a matter of convenience and can be varied in accordance withthe parameters imposed by the environment within which the system isemployed. As a practical matter, stainless-steel serves quitesatisfactorily for this purpose. If so desired, a layer of asbestos, notshown, also can be employed for controlling the transfer of heat withinthe housing 22.

As shown, particularly in FIG. 3, the housing 22 includes a base shell25 having a peripheral portion 26 of an open top configuration. Thisportion of the base shell is defined by an annular bottom wall 27 and anannular outer wall 28. The base shell 25 is closed by a cover shell,generally designated 30.

Within the peripheral portion 26 of the base shell 25 there is provideda second annular wall 32 spaced from and circumscribed by the outer wall28 for defining therebetween an annular heat duct 34 circumscribing thecentral portion, designated 35, of the base shell 25. As bestillustrated in FIG. 2, the annular wall 32 is interrupted at apassageway 36 established between the heat duct 34 and the centralportion 35 which accommodates a flow of heat to the heat duct 34, forreasons which will hereinafter be more fully understood.

The cover shell 30 includes a disk-shaped cover plate 38, which servesto close the central portion 35 of the base shell 25, circumscribed byan annular compartment 40 which functions as a closure member for theannular heat duct 34. The compartment 40 also-is of an annularconfiguration and opens downwardly into the heat duct 34, communicatingtherewith through an annular passage 42. As a practical matter, thecover shell 30 can be fabricated in any suitable manner, and preferablyincludes a plurality of angularly related wall segments 44 welded, orotherwise integrated, and similarly secured to the peripheral portion ofthe disk-shaped cover plate 38. The walls 28 and 32 are coupled with thewall segments 44 through a plurality of interlocking lips, notdesignated, having bearing surfaces mated in a face-to-face engagement,whereby sliding motion therebetween is facilitated. It is to beunderstood that the heat duct 34 and the annular compartment 40 are incontinuous communication through the annular opening 42 so that a flowof heat therebetween can be sustained in a continuous fashion.

As best illustrated in FIGS. 1 and 3, the brackets 24 are fixedlycoupled with the cover plate 38. Accordingly, the cover shell 30 issuspended in a stationary condition. However, for reasons which willhereinafter be more fully understood, the peripheral portion 26 of thebase shell 25, namely the heat duct 34, is supported for rotation aboutan axis of symmetry passing verti cally through the generator 10. Toachieve this, there is provided a rotating spider 45 mounted on astationary base 46. The base 46 is coaxially related to the housing 22and through suitable bearings 48 serves to support the spider 45. Thespider 45 includes a driveshaft 50, extended through the housing 22,from which there radially is extended a plurality of coplanar arms 52upon the distal ends of which there is seated the annular bottom wall 27of the base shell 25. Consequently, the peripheral portion 26 of thebase shell 25 of the housing 22 is supported for rotation, by the spider45, relative to the cover shell 30.

Rotation is imparted to the base shell 25 by an electrically energizablestepping motor 54 coupled to the shaft 50 through a meshed set of bevelgears 56. Hence, by electrically energizing the motor 54, rotationrelative to the cover shell 30 is imparted to the peripheral portion 26of the base shell 25 through the set of bevel gears 56 and the shaft 50.

The central portion 35 of the base shell 25 is subdivided into aplurality of wedge-shaped compartments 58, best shown in FIG. 2. Thesecompartments are formed by a plurality of vertically extended planarwalls 60 extended inwardly along the radius of the base shell 25 from apoint adjacent the annular wall 32 toward the center of the base shell25, terminating at equidistances therefrom. Hence, as shown, thecompartments 58 are arranged in an annular array of eight convergingcompartments open at both the innermost and outermost ends thereof. As apractical matter, the walls 60 are suspended from the cover plate 38 andare mutually spaced at equidistances with the opening at the outermostend being equal to the width of the passageway 36.

Within each of the compartments 58 there is provided a plurality ofboiler tubes 62. Preferably, the boiler tubes 62 are tubular conduits ofpreferred dimensions configured into a bank of series-connected boilertubes of a serpentine configuration. The number of boiler tubes employedin each compartment 58 is deemed a matter of convenience and isdetermined in accordance with prevailing operational conditions.

Each of the boiler tubes 62 receives the working fluid from an intakemanifold 64 coupled therewith through a feeder tube 66. The manifold 64is coupled with the pump 16 by a length of conduit 18, while each of thefeeder tubes 66, in effect, is an extension of one of the boiler tubes62. A suitable one-way check valve 67 is interposed in each of thefeeder tubes 66 for assuring that unidirectional flow characteristicsare imposed on the working fluid as it is delivered from the manifold 64to the boiler tubes 62.

The manifold 64 preferably is formed of tubular stock material into anendless or ring-shaped configuration and is supported externally of thehousing 22. Hence, the feeder tubes 66 are extended through the coverplate 38. The intake manifold 64, the feeder tubes 66, and the boilertubes 62 are united by any suitable technique, including braising,silver soldering and the like.

Each of the boiler tubes 62 further is provided with a discharge tube68, also extending through the cover plate 38, coupled with a dischargemanifold 70, also of an endless or ring-shaped configuration.Preferably, a one-way check valve 72 is interposed between the boilertubes 62 and the discharge manifold 70 for imposing unidirectional flowcharacteristics also on the working fluid as it is discharged from theboiler tubes 62 to the discharge manifold 70.

In view of the foregoing, it should readily be apparent that the workingfluid is delivered by the pump 16 to the vapor generator at the intakemanifold 64, passed through a plurality of one-way check valves 67 intothe boiler tubes 62, thence through the boiler tubes 62 to the dischargemanifold 70, via the plurality of one-way check valves 72.

From the discharge manifold 70 the working fluid, in its vapor phase, isdelivered, via a delivery conduit 74, to the throttle valve 20. It isimportant here to note that the plurality of boiler tubes 62 of thecompartments 58 is coupled with a single intake manifold 64 and a singledischarge manifold 70. Hence, a single delivery to the generator 10,from the pump 16 is accommodated through a length of conduit 18 while asingle delivery conduit 74 is provided for delivering the fluid, in itsheated condition, from the vapor generator 10 to the throttle valve 20.Furthermore, it is important to understand that the heating coils 62 aresuspended from the cover plate 38 in any suitable fashion so long as thefeeder tubes 66 and the discharge tubes 68 are extended through thecover plate 38 and'communicate with the manifolds 64 and 70,respectively.

Heating of the working fluid, prior to its being delivered to thethrottle valve 20, is achieved by means of a rotating fire box,generally designated 76. The fire box is concentrically related to thebase shell 25 and is supported for rotation by the drive shaft 50.

The fire box 76 includes a plurality of vertically aligned gas jets 78projected from the surface of the drive shaft 50, as the shaft extendsthrough the housing 22, and coupled with a suitable source of fuel,preferably a combustible gas, not shown. The jets are connected with thesource of fuel by a tubular conduit 80. As a practical matter, theconduit 80 is concentrically supported within the drive shaft 50 andincludes a swivel coupling, not shown, which permits the conduit 80 torotate relative to the source of gas. Since such couplings are wellknown, a description thereof is omitted. In any event, it is to beunderstood that as the base shell 25 is driven in rotation, rotationalso is imparted to the jets 78 of the fire box 76. Hence, upon lightingthe gas delivered from the jets, rotation of the shaft 50 causes thejets sequentially to be directed into each of the compartments 58whereby a flame of burning gas is caused to heat each bank of the boilertubes 62 in succession.

As best shown in FIG. 2, the tire box 76 also includes a V-shaped heatshield 82 fixed to the drive shaft 50 and radially extended to pointsimmediately adjacent the innermost ends of the walls 60. As a practicalmatter, the gas jets 78 are radially extended through the heat shield 82and are outwardly directed toward the peripheral portions of the baseshell 25 whereby heat generated at the jets is directionally confined.The outwardly directed opening of the heat shield 82 coincides with theinnermost or inwardly directed opening of each of the compartments 58 sothat, in effect, the heat shield 82 serves to complete the innermostportion of each of the compartments 58, for thus isolating each of thecompartments 58 as the bank of the boiler tubes 62 therewithin isheated. Accordingly, it is to be understood that as the drive shaft 50is driven in rotation, successive compartments 58 are caused tocommunicate with the gas jets 78 and, when the fuel delivered thereby isignited, a plurality of radially projected flames is caused to heatboiler tubes 62 within each of the compartments 58.

It is important to understand that the heat shield 82 and the opening 36are in radial alignment. Due to the fact that the heat shield 82 and'theannular wall 32 are fixed to the shaft 50, a fixed positionalrelationship is maintained between the heat shield 82 and the passageway36. Thus the passageway 36 continuously is supported opposite the firebox 76 so that a continuous passage of heated air from the fire box tothe heat duct 34 continuously is provided through each of thecompartments 58 as it is caused to communicate with the fire box.

Since the compartment 40 communicates with the heat duct 34, it is to beunderstood that the compartment 40 also continuously is in communicationwith the fire box 76 through the opening 36 aligned with the fire box 76through one of the compartments 58 being heated. Accordingly, thecompartment 40 continuously is heated as rotation is imparted to thedrive shaft 50, by the motor 54 and the fire box 76 is advanced inrotation in unison with the annular wall 32.

Within the compartment 40 there is disposed a reserve boiler tube 84.Preferably, the boiler tube 84 is of a helical configuration, however,other configurations can be employed equally as well. This boiler tube,of course, continuously is subjected to heat developed within the firebox 76 so that fluid confined therewithin continuously is heated. As aconsequence, the reserve boiler tube 84 is particularly suited as astandby boiler tube which affords the system with an auxiliary source ofheated working fluid in order to preclude an introduction of anoscillating rate of motion at the output of the prime mover 12.

In practice, the boiler tube 84 includes an intake portion 86 coupledwith the delivery conduit 74 through a one-way check valve 88, FIG. 4.The boiler tube 84 further includes a discharge lead 90 also coupledwith the delivery conduit 74. Hence, it should readily be apparent thatso long as the pressures of the fluid confined within the reserve boilertube 84 are maintained at or above the level of the pressure of theworking fluid being delivered through the delivery conduit 74, theone-way check valve 88 is non-conductive. However, in the event thepressure of the fluid confined within the reserve boiler tube 84 dropsbelow that of the working fluid being delivered by the delivery conduit74 the check valve 88 is rendered conductive for delivering fluid fromthe conduit 74 to the reserve boiler tubes 84.

The working fluid delivered to and confined within the reserve boilertube 84 is isolated from the conduit 74 by a selectively actuatablevalve 92 interposed in the discharge lead 90 of the reserve boiler tube84, preferably mid-way between the boiler tube 84 and the deliveryconduit 74. This valve is of any suitable design and is opened andclosed in response to an electrical signal delivered thereto from apressure switch 94, FIG. 1. The pressure switch 94 is interposed in thedelivery conduit 74 and is coupled with the solenoid-operated valve 92through a suitable electrical lead 96. Since pressure switches are wellknown, a detailed description is omitted. In the event a pressure dropof a predetermined magnitude is experienced within the delivery conduit94 it immediately is detected by the pressure switch 94 with a resultingsignal being delivered to the solenoid-operated valve 92, whereupon thevalve 92 is opened for conducting heated fluid from the reserve boilertube 84 to the throttle valve 20, via the delivery conduit 74. Since thereserve boiler tubes 84 continuously are in communication with the tirebox 76, the fluid within the tube continuously is heated. Accordingly,fluid of a predetermined pressure continuously is available for use bythe prime mover 12 in the event a pressure drop is experienced in thedelivery conduit 74.

The pressure switch 94 also is coupled with the stepping motor 54through a suitable control circuit including a lead 98 and asolenoid-activated switch 100. The

switch 100 functions to couple the motor 54 with a suitable source ofvoltage, not shown, in response to a signal received from the pressureswitch 94. Therefore, this circuit serves to assure that a pressureabove a minimal level continuously is imposed on the fluid beingdelivered through the delivery conduits 74 to the throttle valve 20 byadvancing the drive shaft 50 through a predetermined increment ofrotation for thereby bringing the tire into operative communication withthe next-in-line compartment 58 and simultaneously opening the valve 92for supplying heated working fluid to the conduit 74 from the reserveboiler tube 84.

As should readily be apparent, when the fire box 76 is brought intooperative communication with the compartment 58, the working fluidconfined within the boiler tube 62 disposed within the compartment isheated for thus elevating the temperature thereof, preferably to itsphase-change temperature. As a phase change occurs, from a liquid to avapor, the discharge manifold responsively is pressurized through theone-way check valve 72. Upon opening the throttle valve 20, the workingfluid, in its vapor phase, is delivered through the prime mover 12whereupon a pressure drop is experienced in the boiler tube 62 beingheated. Once a pressure drop of a predetermined magnitude is experiencedwithin the delivery conduit 74, it is detected by the pressure switch94. A signal responsively is delivered to the stepping motor 54, throughthe lead 98 and solenoid-activated switch 100, whereupon the motor 54 isenergized for advancing the fire box 76 to the adjacent, next-in-linecompartment 50 for initiating a heating of the bank of boiler tubes 62arranged therewithin. The fluid within the bank of boiler tubes isheated and subsequently delivered to the throttle valve 20, in theaforementioned manner. This cycle, of course, is repeated for each ofthe compartments 58. Of course, during the interval required for heatinga boiler tube 62, for thereby developing the required pressure level, asignal responsively is delivered from the pressure switch 94 to thesolenoid-operated valve 92 so that working fluid, under pressure, isdelivered from the reserve boiler tube 84, through the valve 92, to theprime mover 12 through the throttle valve 20.

For reasons which should readily be apparent, as the working fluid isdelivered to the intake manifold 64, it normally is maintained in itsliquid phase under a pressure substantially less than the pressuredeveloped within the heated boiler tubes 62. Consequently, it isnecessary to effect a charging of the depleted boiler tubes 62subsequent to a cooling thereof. Due to the fact that the fire box 76 isadvanced in an indexing progression, a substantial lapse of time isexperienced between the heating intervals for the boiler tube within agiven compartment. Accordingly, cool-down time is experienced so thatcharging of the boiler tubes 62 in a cooled condition is facilitated.

However, and quite importantly, it is to be understood that theconservation of heat also is deemed highly desirable in order toincrease the total efficiency of the system. Thus the vapor generator 10is provided with a pressure balancing system, generally designated 102,which employs residue pressures for achieving pre-pressurization forfacilitating an efficient operation of the system.

The pressure balancing system 102 includes a plurality of bleeder tubes104 coupled in a communicating relationship with the plurality of banksof boiler tubes 62. In practice, each of the bleeder tubes 104 iscoupled with one of the feeder tubes 66 at a point between one of thecheck valves 67 and the associated boiler tube 62. Thus, the bleedertubes 104, in effect, serve as conduits for exchanging pressures betweenthe various boiler tubes 62.

As a practical matter, the plurality of bleeder tubes 104 radiates froma pressure balancing valve 106 coaxially related to the fire box 76 andsupported at the uppermost or distal end of the drive shaft 50.

The purpose of the pressure balancing valve 106 is to achieve a rapidexchange of pressures between selected boiler tubes of the variouscompartments as indexing of the fire box 76 occurs. Therefore, the valve106 includes a cylindrical housing 108, FIGS. 6 and 7, which receivestherein the adjacent end of the bleeder tubes 104. Within the housingthere is seated a valve plug 1 10 which is fixed to the drive shaft 50and supported for rotation within the housing 108. The plug 110 includesa plurality of transverse bores defining therein a plurality of fluiddelivery channels which extend through the plug and terminate insuitably spaced relationship for accommodating coupling of pairs of thebleeder tubes in communication. Thus, the boiler tubes 62 are caused tocommunicate through the plug 110 in a paired relationship. Of course,each of the boiler tubes 62 is paired with another in accordance withthe instantaneous position of the plug.

It is important to note that each of the diametrically opposed bleedertubes 104 is sealed against communication with any of the other boilertubes 62. Consequently, a flow of working fluid through these bleedertubes 104 is interrupted. The purpose for this relationship is to assurethat pressure cannot be delivered through the pressure balancing valve106 to or from the associate boiler tubes 62. Thus, one of the boilertubes is prepared for heating while the diametrically opposed boilertube is prepared for charging by a delivery of working fluid from theintake manifold. Since the boiler tube 62 being heated always ispositioned at 180 degrees with respect to the boiler tube being charged,charging occurs while the tube is cooled to a maximum extent andtherefore is charged without encountering substantial back pressure.

Accordingly, it is to be understood that where a given vapor generator10 includes eight compartments, the associated pressure balancing valve106 will include three channels for simultaneously coupling six boilertubes 62 in a paired communication, while communication withdiametrically opposed bleeder tubes 104 is interrupted, so that acharging of one boiler tube 62 is accommodated while a heating of thediametrically opposed boiler tube 62 is accomplished. Thus, reduction inthe temperature and the attendant pressures of the working fluidconfined within the boiler tube 62 being charged is maximized in orderthat the effects of back pressure be avoided.

For the sake of illustration, during an operational cycle, the bleedertubes 104 can be considered coupled with the pressure balancing valve106 at eight positions designated A through H, as shown in FIG. 6.Further, assume that the fire box 76 has been indexed for heating theboiler tube associated with the bleeder tube 104 terminating at positionA. Thus the channels 112 couple, in a paired relationship, the boilertubes 62 associated with the bleeder tubes 104 terminating at positionsB and H, C and G, and D and F. Hence, a balanced condition for pressureswithin the pairs of the thus paired boiler tubes is established. Ifdesired, additional channels 112 having lengths sufficient only toextend between adjacent bleeder tubes 104 can be included in the plug sothat adjacent bleeder tubes are brought into momentary communication asthe plug 110 is indexed to its next position, whereby the most recentlyheated boiler tube 104 momentarily communicates with the next boilertube 104 to be heated.

As heat is applied, the pressure is increased in the boiler tube 62connected with the bleeder tube 104, terminating at position A.Simultaneously, a charge of fluid is delivered to the boiler tube 62,via a feeder tube 66, coupled with the bleeder tube 104 terminating atthe position E. Once the boiler tube 62 is heated sufficiently forboiling-off and thus substantially depleting the working fluid from theboiled tube, the motor 54 is activated for again indexing the fire box76. As the fire box is indexed, a rotating motion concurrently isimparted to the plug 110 of the pressure balancing valve 106 for thuscausing the plug to rotate through a distance sufficient for bringingthe bleeder tube 104 terminating at position A into direct communicationwith the bleeder tube 104 terminating at position C. Of course, theboiler tube 62 now being heated is associated with the bleeder tube 104terminating at position B so that no fluid flow is afforded through thisbleeder tube.

Of course, a pressure balance now is established between the pairedboiler tubes 62 associated with the bleeder tubes 104 terminating atpositions A and C, D and H, E and G, respectively, while a charge ofworking fluid is being introduced into the boiler tube 62 associatedwith the bleeder tube 104 terminating at position F. Thus, apre-pressurization of the previously charged boiler tube 62 connectedwith the bleeder tube 104 terminating at position C is effected as apressure reduction occurs in the most recently heated and depletedboiler tube 62 associated with the bleeder. tube 104 terminating inposition A. Since the boiler tube associated with the bleeder tube 104terminating at position H has been pressurized more recently than theboiler tube 62 associated with the bleeder tube 104 terminating atposition D, a pressure balance is established therebetween by permittingthe pressure of the boiler tube associated with position H to bleed intothe boiler tube 62 associated with position D. In a similar fashion, theboiler tube 62 associated with the bleeder tube terminating at positionG is permitted to bleed into the most recently charged boiler tube 62associated with the bleeder tube terminating at position E. Thisvariable pairing of boiler tubes 62 is repeated as the fire box 76 isindexed to communicate with each of the compartments 58 for therebyachieving a stepped pre-pressurization for the charged boiler tubes 62,preparatory to heating, and a stepped de-pressurization, preparatory tocharging depleted boiler tubes 62, is achieved. Thus by employing thepressure balancing valve 106, an encounter with back-pressuresubstantially is avoided and the interval required for achieving a phasechange for the working fluid within the boiler tube 62 is substantiallyreduced, while a maximum use of the heat generated at the fire box 76 isexperienced.

In some instances, the pressures developed within the boiler tubes maybe such as to initiate an escape of gas at the peripheral surface of thepressure balancing valve 106. Accordingly, if so desired, asolenoidoperated valve 114 is included in the bleeder tubes 104, FIG. 8,so that an escape of gas from the bleeder tubes 104 is restricted toselected intervals substantially less than the interval required inachieving; a phase change of the working fluid in a single boiler tube62 disposed within one of the compartments 58. Control is achieved forthe valves 114 by coupling these valves with the switch 100 so that thevalves 114 are actuated once for each step of rotating motion impairedto the fire box 76.

OPERATION OF THE SYSTEM EMPLOYING THE FIRST FORM OF THE VAPOR GENERATORWith the system of the instant invention assembled in the mannerhereinbefore described, it is to be understood that the prime mover 12is driven through a delivery of the working fluid, as a vapor, from thevapor generator through the throttle valve 20. As the vapor escapes fromthe prime mover 12, via a conduit 18, residual heat is given up andcondensation occurs in the condenser 14, whereupon the working fluidundergoes a phase change to a liquid phase. The working fluid now isconducted through the conduit 18 to the pump 16 and thence returned tothe vapor generator 10. The pump 16 is operated at a rate sufficient tosupport an adequate flow-rate for the working fluid as it is deliveredto the intake manifold 64. As the fire box 76 heats a given boiler tube62 a phase change for the working fluid again occurs, resulting in apressurized vapor being delivered to the discharge manifold 70* throughthe one-way check valve 72. The thus pressurized fluid is then conductedvia the delivery conduit 74 to the throttle valve 20 and thereafteragain conducted to the prime mover 12. By controlling the flow-rate ofthe working fluid through the throttle valve 20, the rate of operationof the prime mover 12 is varied.

As the vaporized working fluid is depleted from a given boiler tube 62,as it is heated, a pressure drop is experienced in the delivery conduit74 and detected by the pressure switch 94, whereupon the motor 54 isactivated for indexing the fire box 76 to the adjacent compartment 58,while the solenoid-activated valve 92 is open for delivering heatedfluid from the reserve boiler tube 84, for thus assuring a continuousflow of pressurized working fluid within the system.

Prior to indexing the fire box 76 for thus heating the next-in-lineboiler tube 62, within the adjacent compartment 58, the next-in-lineboiler tube is prepressurized by a delivery of residual pressureacquired from the immediately preceding boiler tube through a channel112 of the plug 110, while a charge of fluid, in its liquid phase, isintroduced into the boiler tube 62 associated with the bleeder tube 104,diametrically opposed to the bleeder tube 104 associated with the boilertube 62 now being heated. Once the temperature of the fluid confinedwithin the boiler tube now being heated attains a predetermined level,the working fluid therewithin undergoes a phase change to a vapor and isdelivered via the check valve 72 to the discharge manifold 70 for thuselevating the pressure of the working fluid within the delivery conduit74.

As the pressure of the fluid within the delivery conduit 74 is elevatedto a predetermined level, the pressure switch 94 initiates a closing ofthe solenoidoperated valve 92. Of course, once the working-fluid withinthe boiler tube-62 being heated is boiled-off and thus depleted, so thata pressure drop is experienced within the delivery conduit 74, the cycleagain is repeated with the pressures developed within the boiler tubesbeing balanced as they successively are connected in variable pairs ofboiler tubes through the bleeder tubes 104.

VAPOR GENERATOR (Second Form) Turning now to FIGS. 9 and 10, therein isdepicted a second form of a vapor generator, which readily can beemployed in a system embodying the principles of the instant invention.

The vapor generator, as illustrated in FIG. 9 and generally designated150, functions in a manner and for a purpose quite similar to that of avapor generator 10 hereinbefore described in detail.

However, as shown in FIG. 9, the boiler tubes 62 of the second formpreferably are of a helical configuration and are arranged in a mutuallyspaced relationship. A gas burner 152, also connected with a source ofcombustible gas, not shown, through a conduit 154 is provided forheating the boiler tubes 62 in succession. As a practical matter, eachof the burners 152 is provided with a suitable pilot light 156 in orderto assure a cyclic relighting of the burners 152 is achieved during theoperation of the generator 150. The intake manifold 64, shown in FIG. 9,while normally not of an annular configuration, performs the functionshereinbefore described, namely that of delivering working fluid to theboiler tubes 62 by way of the feeder tubes 66, in the mannerhereinbefore described. Similarly, the discharge manifold also serves tocouple each of the boiler tubes 62 with the throttle valve 20 in themanner hereinbefore described.

The vapor generator also is provided with a reserve boiler tube 84. Asshown in FIG. 9, this reserve boiler tube is of a helical configurationand is associated with a gas burner 158, coupled with the conduit 154for continuous operation. Since the gas burner 158 is a continuouslyoperating burner, no control is required therefor.

If so desired, a tubular housing 160 can be provided for enclosing ofthe boiler tubes 62 and 84 whereby collection of surplus heat generatedby the burners 158 is collected for delivering a tubular heat duct 162away from the housing 160.

As a practical matter, the reserve boiler tube 84 is housed within acylindrical housing 164 coupled in communication with the heat duct 162so that a discharge of heat into the housing 164 is accommodated forthereby achieving a conservation of energy of heat which normally wouldbe discharged to atmosphere during the operation of any of the boilertubes 62.

The vapor generator 150 also includes a pressure balancing valve quitesimilar in design and function to the pressure balancing valve 106hereinbefore described. However, the valve 170 includes a rotatable plug172 seated within a cylindrical housing 174 and driven by a shaft, notdesignated, extended from a stepping motor 176 for thereby performing afunction similar to that of the pressure balancing valve 106.

The plug 172 includes a pair of relieved peripheral sections formingpressure chambers 178 and 180 adjacent the peripheral surface of theplug. The pressure chambers 178 and 180 are separated by a first land182 of a minimal length while a second land 184, diametrically opposedto the land 182, serves to separate the chambers 178 and 180 atsubstantially the opposite side of the plug 172. However, the secondland 184 is of a substantially greater length than the land 182.Accordingly, the pressure chambers 178 and 180 are eccentrically relatedto the axis of rotation of the plug 172.

As illustrated in FIG. 10, the bleeder tubes 104 terminate at threepositions spaced at equidistances about the periphery of the valve sothat while one of the boiler tubes is being heated the adjacent boilertubes 62 are brought into direct communication through a single channel112 provided for the plug 172. As the motor 176 is activated for drivingthe plug 172 in rotation, the boiler tubes 62 associated with a pair ofcommunicating bleeder tubes 104 are brought into communication forachieving a pressure balance therebetween. However, as the first land182 traverses the surface of the valve housing 174, adjacent the bleedertube 104, a charging of the boiler tube 62 is effected through adelivery of working fluid from the manifold 64 so that as the plug 172is rotated to its next position, the next-inline boiler tube is coupledin direct communication through the channel 112 with the previouslyheated and pressurized boiler tube. For reasons hereinbefore discussed,this cycle is repeated as often as is necessary for pre-pressurizing thenext-in-line and previously charged boiler tube, prior to its beingheated to effect a pressurization and subsequent depletion of theworking fluid from therewithin.

The pressure switch 94 is in direct communication with the fluiddelivery conduit 74, in the manner hereinbefore described with regard tothe vapor generator 10. However, as employed with the vapor generator150, the switch 94 serves to deliver a signal to each of the burners 152in succession, as a pressure drop is experienced within the conduit 74,whereby operation of the burners is initiated in succession forsuccessively heating the boiler tubes associated therewith.

Simultaneously, with the successive initiation of the burners, anindexing of the pressure balancing valve 170 is accomplished byenergizing the motor 176, as hereinbefore discussed. The pressure switch94 also serves to activate the solenoid-control valve 92 coupled withthe reserve boiler tube 84 for effecting a delivery of working fluidunder pressure from the reserve boiler tube 84 to the throttle valve 20via the delivery conduits 74, for reasons hereinbefore fully described.

While not shown, it is to be understood that a lockout circuit can beemployed for rendering the pressure switch 94 inactive during theinitial phase of operation of the vapor generator so that a properheating of the boiler tubes 62 is achieved without experiencing arecycling initiated through a constant low-pressure present within thedelivery conduit 74. Where so employed, such a lock-out switch serves tostabilize operation of the vapor generator until proper temperatureshave been achieved for the system.

OPERATION OF THE SYSTEM EMPLOYING THE SECOND FORM OF THE VAPOR GENERATORWith the pump 16 operating in the manner hereinbefore described, fluid,preferably Freon, in its liquid state is delivered to each of the checkvalves 72 interposed in the feeder tubes 66 in the manner hereinbeforedescribed. Assuming that a charged boiler tube 62, associated with thebleeder tube 104 at a first position of the valve 170, is being heated,the remaining two boiler tubes are in direct communication by way of thepressure chambers 178 and 180 and the interconnecting channel 112 sothat a pressure balance is established therebetween. Once depletion ofthe working fluid from the boiler tube being heated is experienced, apressure drop is experienced in the conduit 74 and is detected by thepressure switch 94. Upon detecting the reduced pressure, the switch 94delivers an initiating signal to the motor 176 for imparting rotation tothe plug 172 causing the land 182 to traverse the opening to thepreceding bleeder tube 104. At this point, the pressure within theboiler tube 62 associated with the preceding bleeder tube 104 isminimized so that a charge of working fluid is delivered thereto.Continued rotation of the plug 172 causes the pressure chamber 178 to bepositioned adjacent the bleeder tube 104 communicating with the nowdepleted boiler tube while the pressure chamber 180 is positionedadjacent the bleeder tube 104 most recently charged so that a pressurebalance is achieved between the boiler tube 62 previously heated and theboiler tube previously charged through the bleeder tubes 104 and thechannel 112. At this juncture, the remaining boiler tube associated withthe pressure balancing valve by the bleeder tube terminating at thesecond land 184 is subjected to heat delivered by one of the burners152.

In order to initiate a cyclic heating of the boiler tubes 82, thepressure switch 94 sequentially activates the burners 152 in a timedsequence with the operation of the pressure balancing valve 170 so thatheating to depletion of given boiler tubes is initiated only after theland 184 separating the pressure chambers 178 and 180 is positioned soas to close the bleeder tube 104 associated with the boiler tube beingheated.

In a manner also quite similar to that hereinbefore discussed, thepressure switch 94 serves to deliver a control signal to thesolenoid-control valve 92 for delivering a flow of pressurized fluidfrom the reserve boiler tube 84 to the throttle 20 via the conduit 74during the intervals between delivery of heated vapor from adjacentboiler tube 62.

In view of the foregoing, it should readily be apparent that the systemof the instant invention provides a practical solution to the problem ofeconomically converting heat to kinetic energy with utmost efficiency.

Although the invention has been herein shown and described in what areconceived to be the most practical and preferred embodiments, .it isrecognized that departures may be made therefrom within the scope of theinvention, which is not to be limited to the illustrative detailsdisclosed.

Having described my invention, what I claim as new and desire to secureby Letters Patent is:

1. An improved system for converting heat to kinetic energy comprising:

A. means including a fluid-driven motor responsive to an introduction offluid under an elevated pres sure for imparting driven motor to aselected power train;

B. fluid control means for introducing to said fluid driven motor fluidat a first given elevated pressure including,

1. a pressure generator comprising, means defining a succession of fluidintake ports, a succession of fluid output ports, and a plurality ofboiler tubes, each of which serves to couple a fluid output port indirect communication with a fluid intake port,

2. fluid delivery means coupled with said intake ports for successivelydelivering to said boiler tubes fluid at a second given pressure,

3. means for heating the boiler tubes in succession,

whereby the pressure of the fluid within successive boiler tubes iselevated to said first given pressure, and

4. fluid transfer means for conveying heated fluid from said outputports to said motor at said first given pressure; and r C. fluid returnmeans for returning the fluid from said fluid driven motor to said fluidcontrol means at said second given pressure.

2. The system of claim 1 wherein the fluid delivery means includes:

A. a condenser coupled with said motor for cooling the fluid, subsequentto an introduction thereof to said motor and prior to a delivery thereofto said boiler tubes;

B. a manifold coupled with said condenser;

C. a plurality of feeder conduits associated with each intake port forcoupling the intake port with said manifold; and

D. a one-way check valve interposed in each of said feeder conduits forimposing unidirectional flow characteristics on the fluid as it isdelivered to the boiler tubes.

3. The system of claim 2 wherein said means for successively heating theboiler tubes includes:

A. a heat generating fire box supported for stepped progression into aheat-exchange relationship with each of said boiler tubes for therebysuccessively heating the boiler tubes;

B. intermittently activated drive means coupled with said fire box forimparting thereto said stepped progression;

C. pressure responsive means interposed in said fluid transfer means andcoupled with said drive means for detecting pressure changes occurringin said fluid transfer means; and

D. means coupled with said pressure responsive means for activating saiddrive means in response to selected pressure changes as they occur insaid fluid transfer means.

4. The system of claim 3 further comprising:

A. means including a reserve boiler tube having opposed ends coupledwith said fluid transfer means, for receiving from and discharging tothe transfer means heated fluid, supported in a continuous heat-exchangerelationship with the fire box, whereby heat continuously is transferredto the reserve boiler from the tire box;

B. a one-way check valve for imposing unidirectional.

flow characteristics on the fluid as it is received by said boiler; and

C. a solenoid controlled valve, interposed between the reserve boilerand the fluid transfer means, coupled with said pressure responsivemeans for limiting discharge of the heated fluid from said reserveboiler to the fluid transfer means.

5. The system of claim 4 wherein said fluidl transfer means includes amanifold and means including a plurality of one-way check valves forcoupling each of said output fluid ports with the manifold.

6. The system of claim 5 further comprising:

a pressure exchange system coupled with each of said boiler tubes,including means for developing in stepped progression a third and afourth pressure within each of said boiler tubes.

7. The system of claim 6 wherein the pressure exchange system includesmeans defining a plurality of bleeder tubes, each communicating with oneof said boiler tubes, and a multi-ported valve operatively coupled withsaid bleeder tubes in a variable relationship for simultaneouslycoupling selected bleeder tubes in variable pairs, whereby the boilertubes are caused to communicate in a variably paired relationship forthereby selectively accommodating a pressure exchange between selectedboiler tubes.

8. The system of claim 7 further comprising a solenoid controlled valveinterposed in each of said bleeder tubes.

9. The system of claim 8 wherein said second pressure is greater thansaid third pressure, and said first pressure is greater than said fourthpressure.

10. In a system for converting heat to energy including a motorresponsive to a flow of heated fluid for providing an output ofmechanical energy, the improvement comprising:

means for establishing a flow of heated fluid including a high-pressuremanifold coupled with said motor for delivering to the motor a flow offluid at a first pressure; a plurality of mutually spaced boiler tubesthe first ends thereof being coupled in direct communication with saidhigh-pressure manifold for serially delivering thereto fluid at saidfirst pressure; a low-pressure manifold coupled in direct communicationwith said plurality of boiler tubes at the second ends thereof fordelivering thereto fluid at a second pressure, lower than said firstpressure; means for controlling the delivery of fluid between saidplurality of boiler tubes and said manifolds; and pressure control meansincluding means for serially heating said plurality of boiler tubes instepped progression for elevating the pressures of the fluid deliveredto the boiler tubes, prior to its delivery therefrom.

11. The improvement of claim 10 wherein each of said boiler tubes is ofa surpentine configuration and said plurality of boiler tubes arearranged in an annular array, with each tube of said array beingextended radially from the center thereof, and said means for seriallyheating said tubes includes a concentric burner coupled with a source ofcombustible fluid and supported for rotation in stepped progression.

12. The improvement of claim 10 wherein said pressure control meansfurther includes a pressure exchange system coupled with each of saidboiler tubes including a plurality of bleeder tubes, each bleeder tubebeing coupled in a communicating relationship with one of said boilertubes, and a multi-ported valve operatively coupled in a variablerelationship with said plurality of bleeder tubes for simultaneouslycoupling selected bleeder tubes in variable, communicating pairs,whereby the boiler tubes are caused to communicate in a variably pairedrelationship for accommodating an exchange of pressure therebetween.

13. An improved system for converting heat to kinetic energy comprising:

A. means including a fluid-driven motor responsive to an introduction offluid under an elevated pressure for imparting driven motion to aselected power train;

B. fluid control means for introducing to said fluid sive boiler tubesis elevated to said first given pressure, and

4. fluid transfer means for conveying heated fluid from said outputports to said motor at said first given pressure;

C. fluid return means for returning the fluid from said fluid drivenmotor to said fluid control means at said second given pressure; and

D. a pressure exchange system coupled with each of said boiler tubes,including means for developing in stepped progression a third and afourth pressure within each of said boiler tubes.

1. An improved system for converting heat to kinetic energy comprising:A. means including a fluid-driven motor responsive to an introduction offluid under an elevated pressure for imparting driven motor to aselected power train; B. fluid control means for introducing to saidfluid driven motor fluid at a first given elevated pressureincluding,
 1. a pressure generator comprising, means defining asuccession of fluid intake ports, a succession of fluid output ports,and a plurality of boiler tubes, each of which serves to couple a fluidoutput port in direct communication with a fluid intake port,
 2. fluiddelivery means coupled with said intake ports for successivelydelivering to said boiler tubes fluid at a second given pressure, 3.means for heating the boiler tubes in succession, whereby the pressureof the fluid within successive boiler tubes is elevated to said firstgiven pressure, and
 4. fluid transfer means for conveying heated fluidfrom said output ports to said motor at said first given pressure; andC. fluid return means for returning the fluid from said fluid drivenmotor to said fluid control means at said second given pressure. 2.fluid delivery means coupled with said intake ports for successivelydelivering to said boiler tubes fluid at a second given pressure, 2.fluid delivery means coupled with said intake ports for successivelydelivering to said boiler tubes fluid at a second given pressure,
 2. Thesystem of claim 1 wherein the fluid delivery means includes: A. acondenser coupled with said motor for cooling the fluid, subsequent toan introduction thereof to said motor and prior to a delivery thereof tosaid boiler tubes; B. a manifold coupled with said condenser; C. aplurality of feeder conduits associated with each intake port forcoupling the intake port with said manifold; and D. a one-way checkvalve interposed in each of said feeder conduits for imposingunidirectional flow characteristics on the fluid as it is delivered tothe boiler tubes.
 3. The system of claim 2 wherein said means forsuccessively heating the boiler tubes includes: A. a heat generatingfire box supported for stepped progression into a heat-exchangerelationship with each of said boiler tubes for thereby successivelyheating the boiler tubes; B. intermittently activated drive meanscoupled with said fire box for imparting thereto said steppedprogression; C. pressure responsive means interposed in said fluidtransfer means and coupled with said drive means for detecting pressurechanges occurring in said fluid transfer means; and D. means coupledwith said pressure responsive means for activating said drive means inresponse to selected pressure changes as they occur in said fluidtransfer means.
 3. means for heating the boiler tubes in succession,whereby the pressure of the fluid within successive boiler tubes iselevated to said first given pressure, And
 3. means for heating theboiler tubes in succession, whereby the pressure of the fluid withinsuccessive boiler tubes is elevated to said first given pressure, and 4.fluid transfer means for conveying heated fluid from said output portsto said motor at said first given pressure; C. fluid return means forreturning the fluid from said fluid driven motor to said fluid controlmeans at said second given pressure; and D. a pressure exchange systemcoupled with each of said boiler tubes, including means for developingin stepped progression a third and a fourth pressure within each of saidboiler tubes.
 4. The system of claim 3 further comprising: A. meansincluding a reserve boiler tube having opposed ends coupled with saidfluid transfer means, for receiving from and discharging to the transfermeans heated fluid, supported in a continuous heat-exchange relationshipwith the fire box, whereby heat continuously is transferred to thereserve boiler from the fire box; B. a one-way check valve for imposingunidirectional flow characteristics on the fluid as it is received bysaid boiler; and C. a solenoid controlled valve, interposed between thereserve boiler and the fluid transfer means, coupled with said pressureresponsive means for limiting discharge of the heated fluid from saidreserve boiler to the fluid transfer means.
 4. fluid transfer means forconveying heated fluid from said output ports to said motor at saidfirst given pressure; and C. fluid return means for returning the fluidfrom said fluid driven motor to said fluid control means at said secondgiven pressure.
 5. The system of claim 4 wherein said fluid transfermeans includes a manifold and means including a plurality of one-waycheck valves for coupling each of said output fluid ports with themanifold.
 6. The system of claim 5 further comprising: a presSureexchange system coupled with each of said boiler tubes, including meansfor developing in stepped progression a third and a fourth pressurewithin each of said boiler tubes.
 7. The system of claim 6 wherein thepressure exchange system includes means defining a plurality of bleedertubes, each communicating with one of said boiler tubes, and amulti-ported valve operatively coupled with said bleeder tubes in avariable relationship for simultaneously coupling selected bleeder tubesin variable pairs, whereby the boiler tubes are caused to communicate ina variably paired relationship for thereby selectively accommodating apressure exchange between selected boiler tubes.
 8. The system of claim7 further comprising a solenoid controlled valve interposed in each ofsaid bleeder tubes.
 9. The system of claim 8 wherein said secondpressure is greater than said third pressure, and said first pressure isgreater than said fourth pressure.
 10. In a system for converting heatto energy including a motor responsive to a flow of heated fluid forproviding an output of mechanical energy, the improvement comprising:means for establishing a flow of heated fluid including a high-pressuremanifold coupled with said motor for delivering to the motor a flow offluid at a first pressure; a plurality of mutually spaced boiler tubesthe first ends thereof being coupled in direct communication with saidhigh-pressure manifold for serially delivering thereto fluid at saidfirst pressure; a low-pressure manifold coupled in direct communicationwith said plurality of boiler tubes at the second ends thereof fordelivering thereto fluid at a second pressure, lower than said firstpressure; means for controlling the delivery of fluid between saidplurality of boiler tubes and said manifolds; and pressure control meansincluding means for serially heating said plurality of boiler tubes instepped progression for elevating the pressures of the fluid deliveredto the boiler tubes, prior to its delivery therefrom.
 11. Theimprovement of claim 10 wherein each of said boiler tubes is of asurpentine configuration and said plurality of boiler tubes are arrangedin an annular array, with each tube of said array being extendedradially from the center thereof, and said means for serially heatingsaid tubes includes a concentric burner coupled with a source ofcombustible fluid and supported for rotation in stepped progression. 12.The improvement of claim 10 wherein said pressure control means furtherincludes a pressure exchange system coupled with each of said boilertubes including a plurality of bleeder tubes, each bleeder tube beingcoupled in a communicating relationship with one of said boiler tubes,and a multi-ported valve operatively coupled in a variable relationshipwith said plurality of bleeder tubes for simultaneously couplingselected bleeder tubes in variable, communicating pairs, whereby theboiler tubes are caused to communicate in a variably paired relationshipfor accommodating an exchange of pressure therebetween.
 13. An improvedsystem for converting heat to kinetic energy comprising: A. meansincluding a fluid-driven motor responsive to an introduction of fluidunder an elevated pressure for imparting driven motion to a selectedpower train; B. fluid control means for introducing to said fluid drivenmotor fluid at a first given elevated pressure including,